JP2014145453A - Bearing pad, bearing device using the same, and rotary machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing pad which effectively cools a pad body thereby easing heat stress and heat deformation and prevents a carryover oil, and to provide a bearing device using the bearing pad and a rotary machine.SOLUTION: A bearing pad includes a pad body 5 which allows a lubrication oil to be disposed in a gap F between itself and an outer peripheral surface 10a of a rotation shaft 10 which rotates around an axis line O and supports the rotation shaft from the outer peripheral side with a pad surface 5b. A lubrication oil supply passage 8 for supplying the lubrication oil to the gap from an outlet part 8b opening in a rotary direction front side area of the pad surface which is located near a rear edge part 5e is formed in the pad body.

Description

  The present invention relates to a bearing pad that rotatably supports a rotating shaft (rotor) of a large-sized rotating machine such as a steam turbine, a gas turbine, a compressor, and a generator, and a bearing device and a rotating machine using the same.

  An example of a bearing device used in a conventional rotating machine is shown in FIGS. The bearing device 100 is called a journal bearing or a tilting pad bearing, and a plurality (four in this example) of bearing pads are arranged at a predetermined interval along the circumferential direction of the axis O of the rotating shaft 101. 102. These bearing pads 102 are accommodated in the housing 103 and support the rotating shaft 101 so as to be rotatable around the axis O. In journal bearings for large rotating machines, lubrication is generally performed by oil bath lubrication in order to enable safe operation of the machine, and there is no lubricating oil between the rotating shaft 101 and the bearing pad 102. An oil film is formed.

  The bearing pad 102 is supported by a pivot 104, and the pivot 104 is known as a point support type for the purpose of preventing the rotation shaft 101 from coming into contact with each other. In the case of the point support type, the bearing pads 102 are supported so as to be swingable in an arbitrary direction around the support point of the pivot 104 having a hemispherical shape, for example, with respect to the corresponding support ring 105. . The bearing pad 102 swings according to the rotation of the rotating shaft 101 and tilts. The inner peripheral surface (sliding surface) 102a of the bearing pad 102 and the outer peripheral surface (sliding surface) of the rotating shaft 101 are caused by the wedge action of the oil film. Oil film pressure is generated with respect to 101a. The load (load) of the rotating shaft 101 is supported by the oil film pressure generated on the bearing pad 102 located on the lower half side of the bearing device 100.

  The lubricating oil supplied from the oil supply hole 106 opened in the housing 103 passes through the inside of the housing 103 from the nozzle 107 located on the rear side in the rotation direction of the bearing pad 102 toward the outer peripheral surface 101 a of the rotary shaft 101. Erupted. Thus, lubrication is performed by forming an oil film between the outer peripheral surface 101a of the rotating shaft 101 and the inner peripheral surface 102a of the bearing pad 102 to reduce friction.

  Here, in the case of a high load condition in which the load on the bearing pad 102 is large, the heat generation at the inner peripheral surface 102 that is the sliding surface of the bearing pad 102 increases, so the temperature difference from the back surface of the bearing pad 102 increases. Thus, thermal deformation occurs in the bearing pad 102 itself. Since the oil film formed on the sliding surface is very thin, the load capacity (weight of the rotating shaft that the bearing can support) as the bearing device 100 is reduced when the pressure deformation and the thermal deformation are combined. was there.

  Here, FIG. 14 shows the analysis result of the temperature distribution of the oil film on the inner peripheral surface 102 a of the bearing pad 102. From this, it can be seen that a region H having the highest temperature is generated near the rear edge of the bearing pad 102 (near the most downstream end portion 102b in the flow direction of the lubricating oil on the inner peripheral surface 102a). Further, in the vicinity of the most downstream end portion 102b in the lubricating oil flow direction on the inner peripheral surface 102a, the region H is wider at the center portion than at both end portions in the width direction of the bearing pad 102 (in the direction of the axis O of the rotating shaft 101). From the distribution, it can be seen that the temperature is higher at the center.

  Further, as an important function of the lubricating oil, in addition to the lubricating function, there is also a cooling function by absorbing and removing the heat generated on the inner peripheral surface 102a as described above. However, the lubricating oil after acting on the inner peripheral surface 102a of one bearing pad 102 flows into the inner peripheral surface 102a of the bearing pad 102 adjacent to the downstream side in the flow direction of the lubricating oil as so-called carry-over oil. End up. For this reason, when the lubricating oil that has been heated by one bearing pad 102 and has a high temperature flows into the inner peripheral surface 102a of the adjacent bearing pad 102 as a carry-over oil, the sliding surface becomes higher in temperature and the oil viscosity decreases. And more severe lubrication such as increased thermal deformation. If this point can be improved, a bearing capable of stably supporting a larger load can be realized.

  In other words, how to prevent this carry-over oil has a direct effect on the lubrication efficiency, which in turn leads to a reduction in the amount of lubricating oil. This reduction in the amount of lubricating oil greatly affects the cost reduction and downsizing of the journal bearing system because the lubricating oil supply device occupies a large specific gravity in the journal bearing system. In addition, with regard to the lubricating oil, there is an agitation loss accompanying the agitation of the lubricating oil due to the rotation of the rotating shaft 101, but this agitation loss can also be reduced by reducing the amount of the lubricating oil, resulting in a reduction in bearing loss.

  As an invention for preventing the temperature rise of the bearing pad 102 and the occurrence of seizure associated therewith, for example, the following Patent Document 1 is disclosed, and as an invention for preventing carry-over oil, for example, the following Patent Document 2 is disclosed. , Each has been proposed.

  The bearing device described in Patent Literature 1 lubricates toward a cooled portion located on the back surface (outer peripheral surface) side corresponding to the downstream portion in the lubricating oil flow direction on the bearing surface (inner peripheral surface) of each tilting pad. A cooling lubricant supply unit for directly supplying oil is provided.

  Further, the bearing device described in Patent Document 2 is elongated in the axial direction on the sliding surface (inner peripheral surface) of the pad at the rear end portion on the downstream side with respect to the moving direction of the lubricating oil accompanying the rotation of the rotating shaft, and An oil guide groove having at least one end opened toward the side plate is provided. Also, a clogging fence that opens in the side plate at a position corresponding to the open end of the oil guide groove, and further projects inward in a state perpendicular to the flow of lubricating oil flowing in the gap between the pad and the side plate. Is provided on the side plate so as to be close to the oil discharge port.

JP 2003-120675 A JP 2003-176818 A

  In the bearing device described in Patent Document 1, although it corresponds to the downstream portion of the lubricating oil flow direction on the high temperature side, each tilting pad is directed toward the back surface side that is relatively cooler than the bearing surface side. Supply cooling oil. Therefore, the downstream portion in the lubricating oil flow direction (see the high temperature region H in FIG. 14) on the bearing surface side where the temperature is locally highest is indirectly cooled, so that a sufficient cooling effect cannot be obtained. there were. In addition, since the cooling is performed from the back side where the temperature is relatively low, there is a problem that thermal stress and thermal deformation cannot be sufficiently relaxed.

  Further, since the load capacity of the bearing device is proportional to the circumferential length of the bearing pad (distance on the sliding surface of the pad in the lubricating oil flow direction), in the bearing device described in Patent Document 2, the sliding surface of the bearing pad is used. There is a problem that the load capacity of the bearing device is reduced due to the provision of the oil guide groove.

  The present invention has been made to solve the above-described problem, and is a bearing device capable of enhancing the cooling of the most downstream end in the lubricating oil flow direction where the temperature is locally highest on the sliding surface of the bearing pad. The purpose is to provide.

In order to achieve the above object, the present invention provides the following means.
The bearing pad according to the present invention includes a pad body that supports the rotating shaft by a pad surface from the outer peripheral side by interposing lubricating oil in a gap between the outer peripheral surface of the rotating shaft that rotates around an axis. Is formed with a lubricating oil supply path for supplying the lubricating oil to the gap from an outlet portion opened near the rear edge on the front side in the rotational direction of the pad surface.

  In the bearing pad, a lubricating oil supply path for supplying lubricating oil from an outlet portion opened near the rear edge portion on the front side in the rotational direction of the pad surface is formed inside the pad main body. Therefore, the rear edge portion of the pad surface that is locally the hottest can be effectively cooled from the inside of the pad main body, and thermal stress and thermal deformation generated in the pad main body can be alleviated.

In addition, by supplying the lubricating oil from the outlet near the rear edge of the pad surface, the lubricating oil that has become hot due to the action on the pad surface can be scraped off from the pad surface, downstream of the lubricating oil flow direction. Carry-over oil flowing into the bearing pad adjacent to the side can be prevented.
In addition, since the low temperature lubricating oil is mixed with the lubricating oil that has become hot due to the action on the pad surface, the temperature of the lubricating oil can be reduced to prevent the cooling action from decreasing and the amount of lubricating oil from increasing. .

In the bearing pad, the lubricating oil supply path may have an inlet portion that opens on a back surface or a side surface of the pad main body.
Thereby, not the lubricating oil that has become hot on the pad surface side but low-temperature lubricating oil on the back surface side or side surface side can be introduced, so that the pad main body can be cooled more effectively.

In the bearing pad, the lubricating oil supply path may be formed so as to pass in the vicinity of the pad surface inside the pad main body.
As a result, the lubricating oil supply passage through which the low-temperature lubricating oil flows is formed at a position closer to the pad surface side where the temperature is relatively higher than the back surface side, so that the pad main body can be cooled more effectively.

In the bearing pad, the lubricating oil supply path may have a meandering portion that meanders inside the pad main body.
Thereby, since the heat transfer area in the meandering portion is increased, the pad main body can be more effectively cooled by heat exchange with the low-temperature lubricating oil flowing in the lubricating oil supply path.

In the bearing pad, the lubricating oil supply path may have a concavo-convex portion whose inner wall surface is formed in a concavo-convex shape.
As a result, the heat transfer area in the concavo-convex portion is increased, and the flow of the lubricating oil is turbulent by the concavo-convex portion to increase the heat transfer rate, so heat exchange with the low-temperature lubricating oil flowing in the lubricating oil supply path Thus, the pad body can be cooled more effectively.

In the bearing pad, a weir may be provided on the front side surface in the rotational direction of the pad body.
Thereby, since the low temperature lubricating oil supplied from the outlet portion of the lubricating oil supply path is also introduced into the inside of this weir, while effectively cooling the side surface on the front side in the rotational direction of the pad body that becomes high temperature, Carryover oil can be prevented more effectively.

In the bearing pad, a plurality of the lubricating oil supply paths may be provided.
Thereby, a pad main body can be cooled over a wider range.

Further, in the bearing pad, the meandering portion may be provided only in the front region in the rotational direction inside the pad main body.
In the bearing pad, the concavo-convex portion may be provided only in a front region in the rotational direction inside the pad main body.
As a result, the heat transfer area in the front region in the rotational direction inside the pad main body, which is relatively hot, can be increased. Therefore, priority is given to the high temperature part of the pad main body by heat exchange with the low temperature lubricating oil flowing in the lubricating oil supply passage. Can be cooled. Therefore, the temperature of the pad main body can be made uniform, and the thermal stress and thermal deformation generated in the pad main body can be alleviated more effectively.

Further, in the bearing pad, the front side surface in the rotational direction may be formed in an uneven surface shape.
As a result, the heat transfer area on the front side surface in the rotational direction of the pad body is increased, so that the heat exchange with the low-temperature lubricating oil introduced into the weir is more effective at the front side in the rotational direction of the pad body that becomes hot. Can be cooled.

In the bearing pad, the pitch in the width direction of the pad main body of the lubricating oil supply path may be smaller at the center than at both ends.
Thereby, the center part which becomes comparatively high temperature rather than the both ends in the width direction of a pad main body can be cooled more preferentially.

  Further, the bearing device of the present invention includes a housing, a plurality of the bearing pads supported in a swingable manner in the housing and arranged in the circumferential direction of the rotating shaft, and the gap between the bearing pads adjacent to each other. And a lubricating oil supply section for supplying the lubricating oil.

  The rotating machine of the present invention includes the rotating shaft and the bearing device that rotatably supports the rotating shaft.

  As a result, the bearing pad can be efficiently cooled, and thermal stress and thermal deformation can be prevented. Therefore, seizure of the bearing device, reduction of load capacity, increase of bearing loss, deterioration of lubricating oil, amount of lubricating oil Increase, cost increase, and increase in size of the apparatus can be prevented.

  According to the present invention, since the lubricating oil is supplied from the outlet portion that opens near the rear edge of the pad surface that is locally the hottest, the pad body is effectively cooled to reduce thermal stress and thermal deformation. And carry-over oil can be prevented.

1 is a schematic cross-sectional view showing a steam turbine according to a first embodiment of the present invention. It is sectional drawing which shows the principal part of an example of the bearing apparatus using the bearing pad which concerns on 1st embodiment of this invention, Comprising: It is a fragmentary sectional view at the time of seeing in the cross section perpendicular | vertical with respect to the axis line of a rotating shaft. . It is the arrow line view which looked at the pad surface from the direction of arrow B in FIG. (A) is sectional drawing of the bearing pad which concerns on the 1st modification of 1st embodiment of this invention, (b) is a bearing pad which concerns on the 1st modification of 1st embodiment of this invention, FIG. It is the arrow line view which looked at the pad surface from the direction of arrow B in FIG. (A) And (b) is sectional drawing of the bearing pad which concerns on the 2nd modification of 1st embodiment of this invention. (A)-(c) is sectional drawing of the bearing pad which concerns on the 3rd modification of 1st embodiment of this invention. It is the arrow line view which looked at the pad surface from the direction of arrow B in FIG. 2 about the bearing pad which concerns on the 4th modification of 1st embodiment of this invention. (A)-(c) is sectional drawing of the bearing pad which concerns on the 5th modification of 1st embodiment of this invention. It is sectional drawing which shows the principal part of an example of the bearing apparatus using the bearing pad which concerns on 2nd embodiment of this invention, Comprising: It is a fragmentary sectional view at the time of seeing in the cross section perpendicular | vertical with respect to the axis line of a rotating shaft. . FIG. 10 is an arrow view of the pad surface viewed from the direction of the arrow BA in FIG. 9. It is the arrow line view which looked at the pad surface from the direction of arrow BA in FIG. 9 about the bearing pad which concerns on the 1st modification of 2nd embodiment of this invention. It is sectional drawing of the bearing apparatus using the conventional bearing pad. It is sectional drawing which shows the AA cross section in FIG. It is a perspective view which shows the analysis result of the temperature distribution of the oil film in the pad surface of the conventional bearing pad.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments and modifications according to a bearing pad of the present invention, a bearing device using the same, and a rotating machine will be described in detail with reference to the drawings. In each embodiment and each modified example, description will be made mainly on differences from the conventional bearing device described with reference to FIGS.

"First embodiment"
First, the steam turbine 20 which concerns on 1st embodiment of this invention is demonstrated with reference to FIG. Here, the steam turbine is an external combustion engine that extracts steam energy as rotational power, and is used by being connected to a generator or the like in a power plant.

  As shown in FIG. 1, the steam turbine 20 includes a casing 30, a regulating valve 40 that adjusts the amount and pressure of steam S flowing into the casing 30, and a power generator (not shown) that is rotatably provided inside the casing 30. A shaft body 50 that transmits power (rotational energy) to a machine such as a machine, a stationary blade 60 held in the casing 30, a moving blade 70 provided on the shaft body 50, and the shaft body 50 and the moving blade 70 are aligned with each other. The main part is a bearing portion 80 that is rotatably supported around O.

  Casing 30 has an internal space hermetically sealed and a flow path for steam S. A ring-shaped partition plate outer ring (stator) 31 through which the shaft body 50 is inserted is firmly fixed to the inner wall surface of the casing 30.

  A plurality of regulating valves 40 are attached to the inside of the casing 30, and each includes a regulating valve chamber 41 into which steam S flows from a boiler (not shown), a valve body 42, and a valve seat 43. When the valve is separated from the valve seat 43, the steam flow path is opened, and the steam S flows into the internal space of the casing 30 through the steam chamber 44.

  The shaft body 50 includes a rotating shaft 10 and a plurality of disks 11 extending in the radial direction of the axis O from the outer peripheral surface 10a (see FIG. 2) of the rotating shaft 10.

  The bearing portion 80 includes a journal bearing (bearing device) 1 and a thrust bearing 81, and supports the shaft body 50 in a freely rotatable manner.

A large number of the stationary blades 60 are arranged radially so as to surround the shaft body 50 to form an annular stationary blade group, and are respectively held by the partition plate outer ring 31 described above. The inner sides in the radial direction of these stationary blades 60 are connected by a ring-shaped hub shroud 61 through which the shaft body 50 is inserted, and the tip ends thereof are disposed with a gap in the radial direction with respect to the shaft body 50. .
The group of annular stator blades composed of the plurality of stator blades 60 is formed at intervals in the axial direction, converts the pressure energy of the steam S into velocity energy, and moves to the rotor blade 70 adjacent to the downstream side. To guide you.

The rotor blade 70 is firmly attached to the outer periphery of the disk 11 included in the shaft body 50. A large number of the moving blades 70 are arranged radially on the downstream side of each annular stationary blade group to constitute the annular moving blade group.
These annular stator blade groups and annular rotor blade groups are grouped into one stage. That is, the steam turbine 20 is configured in six stages.

  Next, the bearing device 1 applied to the steam turbine 20 according to the present embodiment will be described with reference to FIGS.

  As shown in FIG. 2, the bearing device 1 according to the present embodiment includes a plurality of (four in the present embodiment) divided in the circumferential direction of the axis O of the rotary shaft 10 in an annular, U-shaped housing 2 in cross-sectional view. The support ring 3 is fixed. Each support ring 3 has an arc shape when viewed in a line of sight parallel to the axis O, and has a curved plate shape that is wide in the direction of the axis O. A gap C in the radial direction of the axis O is provided between the inner peripheral surface 2 b of the housing 2 and the outer peripheral surface 3 a of the support ring 3. The housing 2 has at least one oil supply hole (not shown) for supplying lubricating oil (see the oil supply hole 106 in FIG. 12), which penetrates from the outer peripheral surface 2a to the inner peripheral surface 2b of the housing 2. Not connected to the lubricating oil supply source and lubricating oil supply pump.

  A plurality (four in this embodiment) of oil supply nozzles (lubricating oil supply units) 4 are fixed integrally with the support ring 3 between the support rings 3 adjacent to each other in the circumferential direction. An introduction port 4 a is opened on the outer peripheral side of the oil supply nozzle 4 so as to face the inner peripheral surface 2 b of the housing 2 in order to introduce the lubricating oil supplied from the oil supply hole and flowing through the gap C into the oil supply nozzle 4. ing. In addition, on the inner peripheral side of the oil supply nozzle 4, a plurality of lubricants (this embodiment) are opposed to the outer peripheral surface 10 a in order to eject the lubricating oil introduced into the oil supply nozzle 4 toward the outer peripheral surface 10 a of the rotating shaft 10. In the embodiment, seven oil supply ports 4b are opened along the direction of the axis O (see FIG. 3).

  A pivot 7 that protrudes toward the inner peripheral side is fixed integrally with the support ring 3 at a substantially central portion of the inner peripheral surface 3b of the support ring 3. The tip on the inner peripheral side of the pivot 7 has a substantially hemispherical shape. There is no.

  Between the oil supply nozzles 4 adjacent to each other in the circumferential direction, the bearing pad 6 having the pad main body 5 can swing on the outer peripheral surface (back surface) 5a with the tip on the inner peripheral side of the pivot 7 as a fulcrum. Further, it is point-supported by a pivot 7 on the inner peripheral side of the support ring 3. Therefore, misalignment between the rotating shaft 10 and the bearing device 1 (a state where the gap F between the outer peripheral surface 10a of the rotating shaft 10 and the inner peripheral surface 5b of the pad main body 5 in the radial direction of the axis O is not uniform). When this occurs, the bearing pad 6 (pad body 5) can follow the rotating shaft 10. The pad main body 5 is only in contact with the pivot 7, and a gap D in the radial direction of the axis O is provided between the outer peripheral surface 5 a of the pad main body 5 and the inner peripheral surface 3 b of the support ring 3. ing.

  Each pad body 5 has an arc shape when viewed in a line of sight parallel to the axis O, and has a curved plate shape that is wide in the direction of the axis O. The curvature radius of the inner peripheral surface (pad surface) 5 b of the pad body 5 is formed to be slightly larger than the curvature radius of the outer peripheral surface 10 a of the rotating shaft 10. That is, the entire pad surface 5 b does not come into contact with the outer peripheral surface 10 a of the rotating shaft 10. The pad surface 5b is made of a soft metal such as white metal (babbit metal).

  Further, a gap E in the circumferential direction of the axis O is between the rotational side surface 5c (the rotational direction front side surface 5c1 and the rotational direction rear side surface 5c2) of the pad body 5 and the rotational direction side surface 4c of the fuel supply nozzle 4. Is provided. The gap E is set to a dimension range in which the pad main body 5 can swing together with the gap D, that is, a dimension range in which the pad main body 5 does not contact the support ring 3 and the oil supply nozzle 4 when the pad main body 5 swings. ing.

  Further, as described above, a gap F in the radial direction of the axis O is formed between the pad surface 5 b of the pad body 5 and the outer peripheral surface 10 a of the rotating shaft 10. The pad main body 5 allows the rotating shaft 10 to rotate about the axis O from the outer peripheral side (the outer peripheral surface 10a side) of the rotating shaft 10 by the pad surface 5b by interposing lubricating oil in the gap F. I support it. Note that the number of the pad main body 5 (bearing pad 6) and the number of the pivots 7 are respectively plural (four in this embodiment) so as to correspond to each other one to one.

  Further, a gap G (see FIG. 3) in the axis O direction is formed between the width direction side surfaces 3d, 4d and 5d of the support ring 3, the oil supply nozzle 4 and the pad body 5 and the side plate 2c of the housing 2. ing.

  A lubricating oil supply path 8 is formed through each pad body 5. The lubricating oil supply passage 8 is provided with two inlet portions 8a (see FIG. 3) that open at substantially the center positions of the side surfaces 5d on both sides of the pad main body 5 and introduce lubricating oil flowing through the gap G. The lubricating oil supply path 8 opens near the rear edge portion 5e on the front side in the rotational direction of the pad surface 5b, and includes a plurality of outlet portions 8b (in this embodiment, jetting and supplying lubricating oil toward the gap F). 7 (see FIG. 3).

  As will be described later, the rear edge 5e of the pad surface 5b has the highest local temperature. Therefore, the outlet portion 8b in the present invention may be opened anywhere as long as the rear edge portion 5e of the pad surface 5b having the locally highest temperature can be cooled. Specifically, the vicinity of the rear edge portion 5e, which is the opening position of the outlet portion 8b on the pad surface 5b of the present invention, is the position of the front edge portion 5f of the pad surface 5b in the rotational direction on the pad surface 5b. Is 0% cd and the position of the trailing edge 5e is 100% cd, it is preferably in the range of 80% cd to 100% cd, and the position closer to 100% cd which is the trailing edge 5e is more preferable. .

  Further, the lubricating oil supply path 8 between the inlet portion 8a and the outlet portion 8b passes through the vicinity of the pad surface 5b inside the pad body 5 in the radial direction of the axis O in the radial direction of the axis O. Is formed. The lubricating oil supply path 8 is formed by machining, electrolytic machining, casting, or the like.

  As will be described later, the pad surface 5b side of the pad body 5 has a relatively higher temperature than the back surface 5a side. Therefore, the lubricating oil supply path 8 in the present invention may pass anywhere as long as all or a part of the lubricating oil supply path 8 can cool the pad surface 5b side that is relatively high in temperature. Specifically, in the pad main body 5, when the position of the pad surface 5 b in the radial direction of the axis O is 0% rd and the position of the back surface 5 a is 100% rd, the vicinity of the pad surface 5 b in the present invention Is preferably in the range of 0% rd to 50% rd, and a position closer to 0% rd that is the pad surface 5b is more preferable.

As shown in FIG. 3, the lubricating oil supply path 8 includes one width-direction lubricating oil supply path 8c that extends linearly so as to penetrate the pad body 5 in the width direction, and is provided with two inlet portions 8a. And communicated with the gap G.
The lubricating oil supply path 8 branches from the width-direction lubricating oil supply path 8c and extends linearly toward the front side in the rotational direction (downstream side in the lubricating oil flow direction), and then immediately before the outlet part 8b. A plurality (seven in this embodiment) of rotational-direction lubricating oil supply passages 8d formed in an L shape by being bent substantially vertically toward the 8b side are provided. These rotational direction lubricating oil supply passages 8d communicate with the width direction lubricating oil supply passage 8c, and also communicate with the gap F through the outlet portion 8b.

  At that time, the pitch P (or density) in the width direction (axis O direction) of the pad main body 5 of the two adjacent rotation direction lubricant oil supply paths 8d is set at both ends of the center portion in the width direction. It arrange | positions so that it may become smaller than a part. Specifically, it is arranged so as to be the smallest at the central portion in the width direction, gradually increasing from the central portion toward both ends, and the maximum at both ends. For example, in the case of this embodiment, as shown in FIG. 3, if the pitch at the center is P1, the pitch between the center and both ends is P2, and the pitch at both ends is P3, then P1 The pitches P are set so as to have a three-stage inclined arrangement of <P2 <P3.

  Next, the operation of the bearing device 1 using the bearing pad 6 of the present embodiment will be described.

  The high-pressure and low-temperature lubricating oil supplied from the lubricating oil supply source and the lubricating oil supply pump flows into the gap C through the oil supply hole opened in the housing 2. The lubricating oil that has flowed into the gap C flows into the oil supply nozzle 4 through the introduction port 4a and also flows into the gap G while flowing mainly along the gap C in the circumferential direction. The lubricating oil that has flowed into the oil supply nozzle 4 flows toward the inner peripheral side through the oil supply nozzle 4, and is then ejected from the oil supply port 4 b toward the outer peripheral surface 10 a of the rotary shaft 10. The low-temperature lubricating oil ejected toward the outer peripheral surface 10a is caught in the rotation of the rotary shaft 10 and guided into the gap F, and the rotational direction of the rotary shaft 10 (the direction of the lubricating oil flow) mainly in the gap F. ) To the front side (downstream side).

  On the other hand, the lubricating oil that has flowed into the gap G flows into the gap F through the gaps D and E, and also flows into the lubricating oil supply path 8 through the inlet portion 8a that opens in the side surface 5d of the pad body 5. . The lubricating oil that has flowed into the lubricating oil supply path 8 flows through the width direction lubricating oil supply path 8c and the rotational direction lubricating oil supply path 8d, and is then ejected into the gap F through the outlet portion 8b. In addition, the air flows in the gap F toward the front side (downstream side) mainly along the rotation direction of the rotary shaft 10 (the flow direction of the lubricating oil).

  Note that the gap F at this time is filled with lubricating oil, but the pad surface 5b of each pad body 5 is substantially stationary, whereas the rotating shaft 10 side rotates at a very high peripheral speed, so a narrow gap In the lubricating oil filled with F, a very large speed difference is generated between the rotating shaft 10 side and the pad main body 5 side. When such a speed difference occurs, a shearing force acts on the lubricating oil, and a viscous force is generated inside the lubricating oil. The wedge effect is generated by the viscous action, the rotation shaft 10 and the inclination formed by the movement of each pad body 5, and the oil film pressure is generated in the lubricating oil in the gap F to support the rotation shaft 10. Can do.

  Here, the pressure distribution applied to the pad surface 5b of each pad body 5 gradually increases in pressure from the rear side in the rotation direction to the front side (upstream side to downstream side in the lubricating oil flow direction) in the gap F. It tends to be maximum at the trailing edge 5e on the front side in the rotational direction of the pad surface 5b (downstream in the lubricating oil flow direction).

  Similarly to this pressure distribution, the shearing force acting on the lubricating oil due to the speed difference between the rotating shaft 10 side and the pad main body 5 side generates heat as well as viscous force inside the lubricating oil. The temperature distribution as shown in FIG. 4 is generated on the pad surface 5b of each pad body 5. Accordingly, a temperature distribution is formed in which the metal temperature of the pad main body 5 becomes maximum at the rear edge portion 5e on the front side in the rotation direction of the pad surface 5b (downstream in the lubricating oil flow direction), and the temperature decreases as the distance from the rear edge portion 5e increases. .

  In addition, when the pressure distribution applied to the pad surface 5b of the pad body 5 is viewed in the width direction (axis O direction), the pressure is highest at the center in the width direction, and the direction from the center to both ends It has a chevron shape in which the pressure gradually decreases as it moves away.

  Due to this pressure distribution, as shown in FIG. 14, a temperature distribution is formed that is highest at the center in the width direction of the pad surface 5b of each pad body 5 and gradually decreases with distance from the center toward both ends. That is, as described above, the region where the temperature is locally highest in the central portion in the width direction (axis O direction) at the rear edge portion 5e of the pad surface 5b in the rotation direction front side (downstream side in the lubricating oil flow direction). (See region H in FIG. 14).

  On the other hand, the lubricating oil at this time has a lubricating action between the rotary shaft 10 and each pad body 5 and also a cooling action for each pad body 5. That is, the low-temperature lubricating oil ejected from the oil supply port 4b of each oil supply nozzle 4 toward the outer peripheral surface 10a of the rotary shaft 10 passes through the clearance F in the rotational direction of the rotary shaft 10 (the flow of the lubricating oil as described above). Each of the pad bodies 5 is convectively cooled from the pad surface 5b side when flowing along the direction). Therefore, the lubricating oil extends from the front edge portion 5f on the pad surface 5b in the rotational direction rear side (upstream side in the lubricating oil flow direction) to the rear edge portion 5e in the rotational direction front side (downstream side in the lubricating oil flow direction). The temperature gradually rises by exchanging heat with the pad body 5. Therefore, the temperature of the lubricating oil is also maximum at the rear edge portion 5e on the front side in the rotational direction of the pad surface 5b (downstream side in the lubricating oil flow direction).

  Conventionally, the lubricating oil that has become hot due to the action on the pad surface 5b in this manner is prevented from flowing into the gap F between the pad body 5 and the rotating shaft 10 adjacent to the front side in the rotational direction. Low temperature lubricating oil was ejected from the oil supply nozzle 4 adjacent to the nozzle. As a result, the high temperature lubricating oil was scraped off from the pad surface 5b and the temperature was lowered by mixing with the low temperature lubricating oil, but the effect of lowering the temperature of the pad main body 5 was not sufficient.

  However, according to the bearing pad 6 of the present embodiment, the lubricating oil supply path 8 is provided in the pad body 5, so that the lubricating oil flows in the width direction lubricating oil supply path 8c and the rotational direction lubricating oil supply path 8d. However, the pad body 5 that has reached a high temperature can be convectively cooled from the inside, and thermal stress and thermal deformation generated in the pad body can be alleviated.

  Further, since the lubricating oil supply path 8 extends to the outlet portion 8b that opens in the vicinity of the rear edge portion 5e on the front side in the rotational direction of the pad surface 5b, it is locally hottest by the low-temperature lubricating oil flowing through the inside. Thus, the trailing edge 5e of the pad surface 5b can be effectively convectively cooled, and thermal stress and thermal deformation generated in the pad main body 5 can be reduced.

Further, since the low temperature lubricating oil is supplied from the outlet portion 8b opened near the rear edge 5e of the pad surface 5b, the high temperature lubricating oil acting on the pad surface 5b is scraped off from the pad surface 5b. Can do. Therefore, it is possible to prevent carry-over oil flowing into the gap F between the pad body 5 adjacent to the front side in the rotational direction (downstream side in the lubricating oil flow direction) and the rotary shaft 10.
In addition, since the low-temperature lubricating oil ejected from the outlet portion 8b is mixed with the lubricating oil that has become hot due to the action on the pad surface 5b, the temperature of the lubricating oil flowing in the gap F is lowered, and the cooling action is reduced. A decrease and an increase in the amount of lubricating oil can be prevented.

  In addition, since the inlet 8a of the lubricating oil supply path 8 is open to the side surface 5d of the pad body 5, not the lubricating oil that has become hot on the pad surface 5b side, but the low-temperature lubricating oil that flows through the gap G, It can be led into the lubricating oil supply path 8 from the inlet 8a. Therefore, it is possible to more effectively convectively cool the pad main body 5 that has reached a high temperature from the inside of the pad main body 5, and to reduce thermal stress and thermal deformation that occur in the pad main body 5.

  Further, since all or a part of the lubricating oil supply path 8 is formed so as to pass in the vicinity of the pad surface 5b inside the pad main body 5, it is relatively more than the outer peripheral surface (back surface) 5a side of the pad main body 5. The low temperature lubricating oil can be convected at a position closer to the pad surface 5b side where the temperature is high. Therefore, the pad main body 5 can be cooled more effectively, and thermal stress and thermal deformation generated in the pad main body 5 can be reduced.

  Further, since a plurality of lubricating oil supply paths 8 (rotational direction lubricating oil supply paths 8d) are provided, the pad main body 5 can be cooled over a wider range, and thermal stress and thermal deformation generated in the pad main body 5 can be reduced. Can be relaxed.

  Further, in the width direction (axis O direction) of the pad main body 5, the pitch P of the lubricating oil supply passage 8 (rotational direction lubricating oil supply passage 8d) is inclined so that the center portion in the width direction is smaller than both end portions. Has been placed. Specifically, the pitch P is set to be minimum at the center in the width direction, gradually increasing from the center toward both ends, and maximum at both ends (P1 <P2 <P3). ). Therefore, it is possible to preferentially cool the central portion, which is relatively hotter than both end portions in the width direction of the pad main body 5, and to reduce thermal stress and thermal deformation generated in the pad main body 5.

  Moreover, according to the bearing apparatus 1 of this embodiment, the said bearing pad 6 (pad main body 5) is provided. Moreover, according to the steam turbine 20 of this embodiment, the said bearing apparatus 1 is provided. Accordingly, the bearing pad 6 (pad body 5) can be efficiently cooled, and thermal stress and thermal deformation can be prevented. Therefore, seizure of the bearing device 1, reduction in load capacity, increase in bearing loss, lubricating oil Deterioration, increase in the amount of lubricating oil, increase in cost, increase in size of the apparatus, and the like can be prevented.

  The lubricating oil supply path 8 has a meandering portion 8e that meanders inside the pad body 5 in its entirety or in part, as in the “first modification of the first embodiment” shown in FIG. It doesn't matter. Specifically, when the position of the front edge portion 5f of the pad surface 5b in the rotation direction is 0% cd and the position of the rear edge portion 5e is 100% cd in the rotation direction, for example, FIG. As shown to a), it is good also considering the linear run-up part 8g which does not meander in the range of 0% cd-50% cd, and the meandering part 8e in the range of 50% cd-100% cd. Or as shown in FIG.4 (b), there is no run-up part 8g, and it is good also considering all in the range of 0% cd-100% cd as the meandering part 8e. The running portion 8g may be curved as long as it does not meander. Further, the meandering direction may be any direction and does not need to be constant from the inlet portion 8a to the outlet portion 8b.

By doing so, the heat transfer area (surface area of the inner wall of the lubricating oil supply passage 8) in the meandering portion 8e is increased as compared with the case without the meandering portion 8e. Thus, the pad main body 5 can be cooled more effectively and heat stress and thermal deformation generated in the pad main body 5 can be reduced.
In addition, the cross-sectional shape of the lubricating oil supply path 8 is not limited to a circle or a square, and the cross-sectional shape may be, for example, a petal shape formed by combining a plurality of curves. As a result, the area of the inner wall surface of the lubricating oil supply passage 8 can be increased, so that the cooling effect can be further improved.

  Similarly, the lubricating oil supply path 8 has, as shown in “second modified example of the first embodiment” shown in FIG. You may have. Specifically, when the position of the front edge 5f of the pad surface 5b in the rotation direction is 0% cd and the position of the rear edge 5e is 100% cd in the rotation direction, for example, FIG. As shown in a), within the range of 0% cd to 50% cd, the inner wall surface of the lubricating oil supply path 8 is a running portion 8g that is not uneven, and the inner diameter is within the range of 50% cd to 100% cd. An uneven portion 8f that changes sequentially in an uneven shape may be formed. Or as shown in FIG.5 (b), there is no run-up part 8g, and uneven | corrugated shape, such as a turbulator and a fin which protrudes inside the lubricating oil supply path 8, in the whole range of 0% cd-100% cd. An uneven portion 8f having a protrusion may be provided. Alternatively, a concave and convex portion 8f that is recessed outside the lubricating oil supply passage 8 like a dimple may be used.

  By doing so, the heat transfer area in the concavo-convex portion 8f is increased as compared to the case without the concavo-convex portion 8f, and the flow of the lubricating oil becomes turbulent by the concavo-convex portion 8f and the heat transfer rate is increased. Therefore, the heat exchange with the low-temperature lubricating oil flowing in the lubricating oil supply path 8 can cool the pad main body 5 more effectively, and the thermal stress and thermal deformation generated in the pad main body 5 can be reduced. .

  Further, as in the “third modified example of the first embodiment” shown in FIG. 6, the lubricating oil supply path 8 has at least one of the meandering portion 8 e and the uneven portion 8 f at the front side in the rotational direction inside the pad body 5. You may have only in the area | region 5h. In addition, the rotation direction front side region 5h inside the pad main body 5 in the present invention specifically refers to the position of the front edge portion 5f of the pad surface 5b in the rotation direction within the pad main body 5 at 0% cd, When the position of the trailing edge portion 5e is 100% cd, it is preferably in the range of 70% cd to 100% cd, and the position closer to 100% cd on the trailing edge portion 5e side is more preferable. For example, within the range of 0% cd to 70% cd is the running portion 8g without the meandering portion 8e and the uneven portion 8f, and only the rotation direction front side region 5h inside the pad main body 5 within the range of 70% cd to 100% cd. In addition, a meandering portion 8e as shown in FIG. 6A or an uneven portion 8f as shown in FIG. 6B may be provided. Or as shown in FIG.6 (c), you may provide both the meandering part 8e and the uneven | corrugated | grooved part 8f only in the rotation direction front side area | region 5h.

  By doing so, the heat transfer area in the front side region 5h in the rotational direction inside the pad main body 5 on the rear edge 5e side that is relatively higher than the front edge 5f side of the pad surface 5b is increased, or the lubricating oil The heat transfer rate can be increased by making the flow of the lubricating oil in the supply passage 8 turbulent. Accordingly, the high temperature portion of the pad main body 5 can be preferentially cooled by heat exchange with the low temperature lubricating oil flowing in the lubricating oil supply path 8, so that the temperature of the pad main body 5 is made uniform, 5 can be more effectively mitigated.

  Further, the lubricating oil supply path 8 has a pad surface where at least one of the meandering portion 8e and the uneven portion 8f is locally the highest temperature as in the “fourth modification of the first embodiment” shown in FIG. You may have only in the vicinity of the rear edge part 5e of 5b, and the vicinity of the center part of the width direction. Furthermore, at least one of the meandering portion 8e and the concavo-convex portion 8f is inclined so as to be larger (more) at the center in the width direction at the rear edge 5e and smaller (less) toward both ends in the width direction. May be.

  In the present invention, the vicinity of the central portion in the width direction may be anywhere as long as it can preferentially cool the central portion in the width direction, which is relatively hotter than both ends in the width direction. Specifically, in the width direction of the pad main body 5, when the position of one end is 0% ad and the position of the other end is 100% ad, it is preferably provided within a range of 25% ad to 75% ad. The position closer to 50% ad which is the central part is more preferable.

  By so doing, as described above, the locally hottest region (see region H in FIG. 14) generated at the center in the width direction of the trailing edge 5e of the pad surface 5b is more preferentially cooled. be able to. Therefore, the temperature of the pad body 5 can be made more uniform, and the thermal stress and thermal deformation generated in the pad body 5 can be alleviated more effectively.

Further, the opening position of the outlet portion 8b is not limited to the pad surface 5b, and the rear edge portion locally having the highest temperature as in the “fifth modified example of the first embodiment” shown in FIG. It only needs to be open in the vicinity of 5e. For example, as shown in FIG. 8A, it may straddle both sides of the pad surface 5b and the rotation direction front side surface 5c1, or as shown in FIG. 8B, it may be on the rotation direction front side surface 5c1. . Alternatively, as shown in FIG. 8C, the outlet portion 8b may be opened in a chamfered portion 5g provided by chamfering a corner portion where the pad surface 5b and the rotation direction front side surface 5c1 are connected.
More specifically, the vicinity of the rear edge portion 5e on the front side surface 5c1 in the rotational direction of the present invention means that the position of the pad surface 5b in the radial direction of the axis O is 0% rd and the position of the back surface 5a is 100. In the case of% rd, as shown in FIG. 8 (b), it is preferable to be within the range of 0% rd to 50% rd on the front side surface 5c1 in the rotation direction, and to 0% rd which is the pad surface 5b. The closer the position, the more preferable.

"Second embodiment"
Next, a second embodiment relating to a bearing pad applied to a bearing device for a steam turbine according to the present invention will be described with reference to FIGS.

  The bearing pad of this embodiment is different from the first embodiment in the configuration of the bearing pad, and specifically, the configuration around the front side surface in the rotational direction of the pad body is different. Therefore, in the present embodiment, only the periphery of the front side surface in the rotational direction of the pad body will be described with reference to FIGS. 9 and 10, and the same components as those in the first embodiment are denoted by the same reference numerals. The description is omitted. In FIG. 9, the configuration other than the rotating shaft 10, the bearing pad 6 </ b> A, and the oil supply nozzle 4 is omitted for convenience.

  As shown in FIGS. 9 and 10, the bearing pad 6 </ b> A of the bearing device 1 </ b> A in the present embodiment is provided with a weir 90 on the front side surface 5 c 1 in the rotational direction of the pad body 5. The weir 90 has substantially the same dimensions as the pad body 5 in the width direction and has a substantially L shape in cross-sectional view extending in the width direction, and a substantially rectangular shape fixed to both ends of the weir body 90a in the width direction. And a weir side plate portion 90b. Therefore, the dam 90 has a shape in which two surfaces facing the two adjacent sides among the four sides of the substantially rectangular dam side plate portion 90b are opened.

  The weir 90 is integrally fixed to the front side surface 5c1 in the rotational direction of the pad body 5 so that one of the two open surfaces faces the outer peripheral surface 10a side of the rotating shaft 10. Has been. As a result, the outer peripheral surface 10 a side of the rotary shaft 10 is opened inside the weir 90, and a cavity 90 c surrounded by the rotation direction front side surface 5 c 1 and the inner wall surface of the weir 90 is formed. The shape and dimensions of the weir 90 are set so that the weir 90 does not contact the fuel supply nozzle 4 and the rotating shaft 10 even when the pad main body 5 swings around the pivot 7 tip.

  Further, the outlet portion 8 b of the lubricating oil supply path 8 is opened on the front side surface 5 c 1 in the rotational direction in the vicinity of the rear edge portion 5 e of the pad main body 5. Thereby, the lubricating oil supply path 8 communicates with the cavity 90c.

  As in the first embodiment, in this embodiment, the outlet 8b is opened at any position where the rear edge 5e of the pad surface 5b that is locally hottest can be cooled. May be. Specifically, the vicinity of the rear edge 5e, which is the opening position of the outlet portion 8b in the present embodiment, is 0% of the position of the pad surface 5b in the radial direction of the axis O on the front side surface 5c1 in the rotational direction. When the position of the rd and the back surface 5a is 100% rd, the position is preferably in the range of 0% rd to 25% rd, and the position closer to 0% rd that is the pad surface 5b is more preferable.

  According to the present embodiment, the low-temperature lubricating oil ejected from the outlet portion 8 b of the lubricating oil supply path 8 is once filled into the cavity 90 c formed inside the weir 90. Therefore, in the present embodiment, in addition to the operational effects obtained in the first embodiment, the low-temperature lubricating oil filled in the cavity 90c causes the front side in the rotational direction of the pad main body 5 that has become hot to move forward in the rotational direction. It can cool effectively from the side surface 5c1 side.

  Furthermore, the lubricating oil that has cooled the front side of the pad body 5 in the rotational direction flows out from the cavity 90c to the outer peripheral surface 10a side of the rotary shaft 10 that is opened. At this time, the lubricating oil flowing out from the cavity 90c of the weir 90 can be scraped off from the pad surface 5b by acting on the pad surface 5b in the gap F and flowing at a high temperature. Therefore, it is possible to more effectively prevent carry-over oil flowing into the gap F between the bearing pad 6A (pad body 5) adjacent to the front side in the rotational direction (downstream side in the lubricating oil flow direction) and the rotary shaft 10. it can.

  Further, since the low temperature lubricating oil that has flowed out from the cavity 90c of the weir 90 is mixed with the lubricating oil that has been heated at the pad surface 5b, the temperature of the lubricating oil flowing in the gap F is further reduced. Further, it is possible to more effectively prevent the cooling action from decreasing and the lubricating oil amount from increasing.

  Note that the front side surface 5c1 in the rotational direction may be formed in an uneven surface shape such as a wave shape as in the “first modification of the second embodiment” shown in FIG. In addition, it is not restricted to a wave shape, and other uneven surface shapes may be used as long as the surface area of the front side surface 5c1 in the rotation direction is larger than that of a flat surface. For example, protrusions and fins that protrude forward in the rotational direction, or dimples that are recessed rearward in the rotational direction may be provided to form an uneven surface. Further, it is not always necessary to make the entire front side surface 5c1 in the rotational direction into a concavo-convex surface, and it may be a part thereof.

  By doing so, the heat transfer area on the front side surface 5c1 in the rotational direction of the pad main body 5 is increased, so that the front side in the rotational direction of the pad main body 5 at a relatively high temperature is filled in the cavity 90c of the weir 90. The heat exchange with the low-temperature lubricating oil can cool down more effectively, and the thermal stress and thermal deformation generated in the pad main body 5 can be reduced.

The technical scope of the present invention is not limited to the above embodiments, and various changes and combinations can be added without departing from the spirit of the present invention.
For example, in the above-described embodiment, the steam turbine 20 is described as having six stages when the annular stator blade group and the annular rotor blade group are combined into one stage. However, the steam turbine 20 is not necessarily limited to this. You may comprise by the number of steps other than a step.

  In the above embodiment, the bearing devices 1 and 1A have a plurality of support rings 3 fixed in the housing 2, and a plurality of oil supply nozzles 4 between the support rings 3 adjacent to each other in the circumferential direction. It has been described that the pad main body 5 is supported by the pivot 7 projecting from the inner peripheral surface 3b. However, this need not necessarily be the case, and the pad main body 5 may be supported by omitting the support ring 3 and projecting the pivot 7 on the inner peripheral surface 2 b of the housing 2. In this case, the oil supply nozzle 4 may be fixed to the housing 2 and supplied directly from the lubricant supply source.

In the above embodiment, it has been described that four each of the support ring 3, the oil supply nozzle 4, the pad main body 5 (bearing pad 6), and the pivot 7 are provided, but this need not necessarily be the case. Other numbers may be used.
In the above-described embodiment, it has been described that seven oil supply ports 4b of each oil supply nozzle 4 are provided. However, the number is not necessarily limited to this, and the number may be other than seven.

  In the above embodiment, it has been described that the pad main body 5 is point-supported at the tip of the inner circumference side of the pivot 7 having a substantially hemispherical shape. However, this need not necessarily be the case, and the pad main body 5 is supported in a swingable manner. If possible, other shapes may be used, and support may be performed by a method other than point support.

  In the above embodiment, the opening position of the inlet portion 8a has been described as the substantially central position of the side surface 5d of the pad main body 5. However, this need not necessarily be the case, and the lubricating oil having a high temperature on the pad surface 5b side is not necessarily required. However, it may be a position where low temperature lubricating oil can be introduced. For example, it may be the side surface 5d other than the substantially central position, or any of the outer peripheral surface (back surface) 5a and the side surface 5c (the rotation direction front side surface 5c1 and the rotation direction rear side surface 5c2) of the pad main body 5.

  Further, in the above embodiment, it has been described that the entrance portion 8a is opened in total, two on each side of the side surface 5d of the pad body 5, but this is not necessarily limited, and the side surface 5c and the side surface 5d are not limited to this. Only one opening may be provided on any one surface. Alternatively, three or more inlet portions 8a may be provided on at least one of the side surface 5c and the side surface 5d.

Moreover, although the said embodiment demonstrated providing one width direction lubricating oil supply path 8c, it does not necessarily need to be this limit and may provide two or more. Similarly, in the above-described embodiment, it has been described that the seven outlet portions 8b and the rotational direction lubricating oil supply passages 8d are provided. However, the number of the outlet portions 8b and the rotational direction lubricating oil supply passages 8d are not necessarily limited, and the number thereof may be changed as appropriate. In these cases, the inlet portion 8a, the outlet portion 8b, the width direction lubricating oil supply passage 8c, and the rotational direction lubricating oil supply passage 8d may be appropriately connected.
Alternatively, all of the inlet portion 8a, the outlet portion 8b, the width direction lubricating oil supply path 8c, and the rotational direction lubricating oil supply path 8d do not have to be connected as one lubricating oil supply path 8, and the one pad body 5 has the same structure. A plurality of independent lubricating oil supply paths 8 may be provided.

  In the above embodiment, the lubricating oil supply path 8 (the width direction lubricating oil supply path 8c and the rotational direction lubricating oil supply path 8d) has been described as being linear or L-shaped, but this is not necessarily limited. As shown in FIG. 8 (a), it may be formed in other shapes such as a letter shape (an angle other than vertical), or as shown in FIG. A part may be curved and formed.

  In the above-described embodiment, the width-direction lubricating oil supply path 8c and the rotation-direction lubricating oil supply path 8d have been described as extending in the width direction and the rotation direction. May extend in a direction inclined with respect to the width direction and the rotation direction.

  In the above embodiment, the pitch P of the lubricating oil supply passage 8 in the width direction is described as being inclined so that the central portion is smaller than both ends (for example, three stages of P1 <P2 <P3). did. However, it is not necessarily limited to this, and conversely, the central portion may be larger than the both end portions (for example, P1> P2> P3), or even at an equal pitch (for example, P1 = P2 = P3). Good. Or it is good also as an unequal pitch which is not inclination arrangement | positioning, and good also as arrangements other than 3 steps, such as 2 steps | paragraphs and 4 steps | paragraphs.

In the second embodiment, it has been described that the weir 90 extends in the width direction with substantially the same dimensions as the pad body 5 in the width direction, but this need not necessarily be the case, and the width dimension is larger than that of the pad body 5. It can be small.
In the second embodiment, the weir body 90a has been described as having a substantially L shape in cross section. However, this is not necessarily limited to this, and other cross sectional shapes such as a substantially J shape in cross section may be used.
In the second embodiment, the weir side plate portion 90b has been described as having a substantially rectangular shape. However, this is not necessarily limited to this, and the cavity corresponds to the cross-sectional shapes of the front side surface 5c1 in the rotation direction and the weir body portion 90a. Other shapes may be used as long as 90c can be formed.

  In the second embodiment, the weir 90 is described as having a shape that covers only the pad surface 5b side (near the rear edge 5e) of the front side surface 5c1 in the rotational direction, as shown in FIG. However, this need not necessarily be the case. After the low temperature lubricating oil ejected from the outlet portion 8b is once filled in the cavity 90c and the front side in the rotational direction of the pad body 5 is cooled, the rotational shaft 10 What is necessary is just to be able to flow out to the outer peripheral surface 10a side. For example, when the position of the pad surface 5b in the radial direction of the axis O is 0% rd and the position of the back surface 5a is 100% rd on the rotation direction front side surface 5c1, the entire rotation direction front side surface 5c1 (0 % Rd to 100% rd) and the inner peripheral half (0% rd to 50% rd) may be provided. At this time, it is preferable to provide at least the 0% rd position on the side of the pad surface 5b that becomes high temperature.

  In the above embodiment, the steam turbine 20 has been described as an example. However, the present invention is not necessarily limited to this, and a bearing that rotatably supports the rotating shaft, such as a gas turbine, a compressor, or a generator. The present invention can be applied to other types of rotary machines including a pad and a bearing device.

1 Bearing device (journal bearing)
1A Bearing device 2 Housing 2a Outer peripheral surface 2b Inner peripheral surface 2c Side plate 3 Support ring 3a Outer peripheral surface 3b Inner peripheral surface 3d Side surface (width direction side surface)
4 Lubrication nozzle (lubricant supply part)
4a Inlet 4b Refueling port 4c Side surface (side surface in rotation direction)
4d side (width direction side)
5 Pad body 5a Outer peripheral surface (back surface)
5b Inner peripheral surface (pad surface)
5c Side surface (side surface in rotation direction)
5c1 side surface (front side surface in the rotational direction)
5c2 side surface (back side surface in the rotational direction)
5d side (width direction side)
5e Rear edge portion 5f Front edge portion 5g Chamfered portion 5h Rotational direction front side region 6 Bearing pad 6A Bearing pad 7 Pivot 8 Lubricating oil supply passage 8a Inlet portion 8b Outlet portion 8c Width direction lubricating oil supply passage 8d Rotational direction lubricating oil supply passage 8e Meandering portion 8f Concavity and convexity portion 8g Running portion 10 Rotating shaft 10a Outer peripheral surface 20 Steam turbine 90 Weir 90a Weir body portion 90b Weir side plate portion 90c Cavity C Clearance D Clearance E Clearance F Clearance G Clearance H Region (High temperature region)
O Axis P Pitch P1 Pitch P2 Pitch P3 Pitch

Claims (13)

Comprising a pad main body that supports the rotating shaft from the outer peripheral side with a pad surface by interposing lubricating oil in a gap between the outer peripheral surface of the rotating shaft that rotates around the axis,
A bearing for supplying a lubricating oil to the gap from an outlet opening in the vicinity of a rear edge on the front side in the rotational direction of the pad surface is formed inside the pad main body. pad.   The bearing pad according to claim 1, wherein the lubricating oil supply path has an inlet portion that opens on a back surface or a side surface of the pad main body.   The bearing pad according to claim 1, wherein the lubricating oil supply path is formed so as to pass in the vicinity of the pad surface inside the pad main body.   The bearing pad according to any one of claims 1 to 3, wherein the lubricating oil supply path has a meandering portion that meanders inside the pad main body.   The bearing pad according to any one of claims 1 to 4, wherein the lubricating oil supply passage has an uneven portion whose inner wall surface is formed in an uneven shape.   The bearing pad according to claim 1, further comprising a weir on a front side surface in the rotation direction of the pad main body.   The bearing pad according to claim 1, wherein a plurality of the lubricating oil supply paths are provided.   5. The bearing pad according to claim 4, wherein the meandering portion is provided only in a front region in the rotational direction inside the pad main body.   The bearing pad according to claim 5, wherein the concavo-convex portion is provided only in a front region in the rotational direction inside the pad main body.   The bearing pad according to claim 6, wherein a front side surface in the rotation direction is formed in an uneven surface shape.   The bearing pad according to claim 7, wherein a pitch of the lubricating oil supply path in the width direction of the pad main body is smaller at the center than at both ends. A housing;
The bearing pad according to any one of claims 1 to 11, wherein the bearing pad is swingably supported in the housing, and a plurality of bearing pads are arranged in a circumferential direction of the rotating shaft.
A lubricating oil supply section that supplies the lubricating oil to the gap from between the bearing pads adjacent to each other;
A bearing device comprising: The rotating shaft;
The bearing device according to claim 12, which rotatably supports the rotating shaft;
A rotating machine characterized by comprising:

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